DK172177B1

DK172177B1 - Axial seal

Info

Publication number: DK172177B1
Application number: DK133995A
Authority: DK
Inventors: Joern Holger Klausen; Tage Joergensen; Ingvard Mosby Madsen; Peter Froeslev
Original assignee: Danfoss As
Priority date: 1995-11-27
Filing date: 1995-11-27
Publication date: 1997-12-15
Also published as: DK133995A; EP0864047A1; AU7621796A; WO1997020145A1

Description

i DK 172177 B1in DK 172177 B1

Den foreliggende opfindelse angår en aksial tætning i en pumpe eller motor, der omfatter et hus med sidevægge, der afgrænser en aksial udstrækning for et kammer, og af hvilke sidevægge i det mindste én har et indløb og valgfrit et udløb, hvilken pumpe eller motor tillige omfatter en omdrejningsaksel, der strækker sig gennem i det mindste et 5 akselhul i den ene sidevæg, et roterende element, der befinder sig mellem sidevæggene, og som har en første sideflade, der er modstående den ene sidevæg, og en anden sideflade, der er modstående den anden sidevæg, hvilket roterende element er beregnet til at blive roteret af omdrejningsakslen, og mindst ét tætningselement, der befinder sig mellem og ligger an mod en inderside af en sidevæg og en sideflade for det roterende ele-10 ment.The present invention relates to an axial seal in a pump or motor comprising a housing with sidewalls defining an axial extension of a chamber and at least one of which has an inlet and optionally an outlet, which pump or motor also comprises a rotary shaft extending through at least one shaft hole in one side wall, a rotating member located between the side walls having a first side face opposite one side wall, and a second side face which is opposed to the second side wall, which rotating element is intended to be rotated by the pivot shaft, and at least one sealing element located between and abutting an inside of a side wall and a side surface of the rotating element.

DE 26 06 172 beskriver en pumpe med en tætning af ovennævnte type. Pumpen omfatter et pumpehus med et orbiterende tandhjul, der bliver drevet af en aksel. Et tætningselement er anbragt mellem en sideflade for tandhjulet og en sidevæg for pumpe-15 kammeret. Tætningselementet er beregnet til at opretholde et givet tryk på tandhjulet i retning mod en anden sidevæg således, at risikoen mindskes for lækage mellem den første sideflade for det orbiterende tandhjul og den første sidevæg for pumpekammeret.DE 26 06 172 discloses a pump having a seal of the above type. The pump comprises a pump housing with an orbiting sprocket driven by a shaft. A sealing member is disposed between a side face of the gear wheel and a side wall of the pump chamber. The sealing member is intended to maintain a given pressure on the gear toward a second sidewall so as to reduce the risk of leakage between the first sidewall of the orbiting gear and the first sidewall of the pump chamber.

Pumpen med tætning besidder imidlertid den ulempe, at tætningen mellem den første 20 sideflade og den første sidevæg er meget afhængig af, at overfladerne er i tæt anlæg med hinanden. Så længe omdrejningshastigheden af akslen og dermed af tandhjulet er begrænset, og så længe det medium, der pumpes, har en tilstrækkelig høj viskositet, er risikoen for lækage lille. Såfremt omdrejningshastigheden forøges, og/eller såfremt det medium, der pumpes, har en lavere viskositet, øges risikoen for lækage. Såfremt lækage 25 finder sted, er der endvidere risiko for at akslen og eventuelle lejer for akslen kan beskadiges, f.eks. ved korrosion, af det medium, der pumpes. Endvidere finder tætningen sted ved metallisk flade mod metallisk flade og kræver således, at det medium, der pumpes, har smørende egenskaber.However, the sealing pump has the disadvantage that the seal between the first 20 side surface and the first side wall is highly dependent on the surfaces being in close contact with one another. As long as the speed of rotation of the shaft and thus of the gear is limited and as long as the medium being pumped has a sufficiently high viscosity, the risk of leakage is small. If the speed of rotation is increased and / or if the medium being pumped has a lower viscosity, the risk of leakage increases. Furthermore, if leakage 25 occurs, there is a risk that the shaft and any bearings for the shaft may be damaged, e.g. by corrosion, of the medium being pumped. Furthermore, the sealing takes place at metallic surface against metallic surface and thus requires that the medium being pumped has lubricating properties.

30 Disse ulemper har ikke tidligere været erkendt. Med anvendelsen af pumpemedier såsom vand, der har en lav viskositet i forhold til mere konventionelle pumpemedier, og 2 DK 172177 B1 som eventuelt tillige kan beskadige omdrejningsaksel og lejer, og med nødvendigheden af pumper med højere omdrejningstal for at etablere tilstrækkeligt tryk i medier med lav viskositet, er der opstået problemer med holdbarheden, driftssikkerheden og effektiviteten af kendte pumper.30 These disadvantages have not been previously recognized. With the use of pump media such as water having a low viscosity over more conventional pumping media, and 2 DK 172177 B1 which may also damage the shaft and bearings, and with the need for higher speed pumps to establish sufficient pressure in low media viscosity, problems with the durability, reliability and efficiency of known pumps have arisen.

55

Det er således formålet med den foreliggende opfindelse at tilvejebringe en tætning, der yder en større grad af tætning end overfladetætning mellem sidefladen for et roterende element såsom et roterende tandhjul og sidevæggen for pumpekammeret, således at lækage til omdrejningsakslen og dermed til omgivelserne fra pumpekammeret undgås.Thus, it is the object of the present invention to provide a seal that provides a greater degree of seal than surface seal between the side surface of a rotating member such as a rotating gear and the side wall of the pump chamber so as to avoid leakage to the shaft and thus to the surroundings of the pump chamber.

1010

Dette formål opnås med en tætning, der er særpræget ved, at tætningselementet strækker sig rundt om omdrejningsakslen, og at tætningselementet i radial retning er anbragt mellem omdrejningsakslen og indløbet, valgfrit udløbet.This object is achieved with a seal, which is characterized in that the sealing element extends around the rotational shaft and that the sealing element is radially disposed between the rotational shaft and the inlet, optionally the outlet.

15 En tætning med disse kendetegn er effektiv til tætning mellem et pumpekammer og en omdrejningsaksel, hvor det er påkrævet, at det medium, der pumpes, ikke ved lækage ledes til omdrejningsakslen, til eventuelle lejer for omdrejningsakslen eller til omgivelserne. Tætningen er generelt egnet til tætning ved omdrejningsaksler og specielt velegnet til pumper med et højt omdrejningstal for omdrejningsakslen. Tolerancer mellem 20 sidefladerne for det roterende element og sidevæggene for pumpehuset kan fastholdes uafhængigt af, om der anvendes pumper eller motorer med lave eller høje omdrejningstal.A seal with these characteristics is effective for sealing between a pump chamber and a rotary shaft, where it is required that the medium being pumped is not guided by leakage to the rotary shaft, to any bearings of the rotary shaft or to the surroundings. The seal is generally suitable for sealing at rpm and particularly suitable for pumps with a high rpm for the rpm. Tolerances between the 20 side surfaces of the rotating element and the side walls of the pump housing can be maintained regardless of whether pumps or motors with low or high rpm are used.

Ved pumpning af væsker med lav viskositet, det vil sige viskositet, der er mindre end 25 mange hydraulikolier, er tætningen ifølge opfindelsen også velegnet. Lækage som følge af utilstrækkeligt anlæg mellem en sideflade for et roterende element og en sidevæg for pumpekammeret undgås og risiko for kapillarrørs-virkning mellem sådanne flader eli-mineres.Tætningen forhindrer således i stilstand, at pumpemedie ledes til omdrejnings-akslen.When pumping liquids of low viscosity, i.e. viscosity less than 25 many hydraulic oils, the seal according to the invention is also suitable. Leakage due to insufficient contact between a side surface of a rotating element and a side wall of the pump chamber is avoided and the risk of capillary tube action between such surfaces is eliminated. The seal thus stops the pump medium from being led to the shaft.

30 3 DK 172177 B1 I en foretrukket udførelsesform er tætningen ifølge opfindelsen særpræget ved, at henholdsvis mindst den ene af den første henholdsvis den anden af sidefladerne på det roterende element er forsynet med et spor, der strækker sig omkring rotationsakslen, og at et tætningselement er anbragt i sporet og er i anlæg med den modstående sidevæg.In a preferred embodiment, the seal according to the invention is characterized in that at least one of the first and the other, respectively, of the side surfaces of the rotating element is provided with a groove extending around the rotational shaft and that a sealing element is placed in the groove and abutting the opposite side wall.

5 I en yderligere foretrukket udførelsesform er tætningen ifølge opfindelsen og ifølge den ovenfor anførte foretrukne udførelsesform særpræget ved, at tætningselementet består af et slidelement og et hosliggende elastisk element, at det elastiske element har en mindste diameter, der er mindre end eller lig den mindste diameter af sporet, at det elastiske 10 element har en største diameter, der er mindre end en største diameter af sporet, at det elastiske element er anbragt i en bund for sporet, og at slideelementet er anbragt mellem det elastiske element og en åbning for sporet. Slidelement og elastisk element kan være sammenbygget til samme enhed.In a further preferred embodiment, the seal according to the invention and according to the above preferred embodiment is characterized in that the sealing element consists of a wear element and an adjacent elastic element, that the elastic element has a minimum diameter smaller than or equal to the smallest diameter. of the groove, that the elastic member has a maximum diameter smaller than a larger diameter of the groove, that the elastic member is placed in a bottom for the groove, and that the slide member is disposed between the elastic member and an opening for the groove. Wear element and elastic element can be joined to the same unit.

15 Et tætningselement, der består af en kombination af et slidstærkt element og et elastisk element, har vist sig at være anvendelig til at opnå tilstrækkelig tætning i den type pumper eller motorer, som tætningen ifølge opfindelsen primært finder anvendelse i. Det slidstærke tætningselement kan endvidere være belagt med eller være fremstillet af et materiale, der nedsætter friktionen mellem ringen og sidevæggen, såsom polytetraflou-20 rethen f.eks. som forhandlet under varemærket teflon®, alternativt PEEK.A sealing element consisting of a combination of a durable element and an elastic element has been found to be useful in obtaining sufficient sealing in the type of pumps or motors in which the seal according to the invention primarily applies. The durable sealing element can furthermore be coated with or made of a material which reduces the friction between the ring and the sidewall, such as polytetrafluoroethane e.g. as negotiated under the trademark teflon®, or PEEK.

Det er imidlertid vigtigt, at den mindste diameter af det elastiske element er mindre end eller lig den mindste diameter af sporet, således at det elastiske element, når dette er anbragt i sporet, ligger an mod den inderste diameter af sporet og ikke ligger an mod 25 den yderste diameter af sporet.However, it is important that the smallest diameter of the elastic member is less than or equal to the smallest diameter of the groove, so that the elastic member, when disposed in the groove, abuts the inner diameter of the groove and does not abut the 25 the outer diameter of the groove.

Pumpemedium under tryk, der ledes mod tætningselementet vil blive ledt ind i sporet ved dettes yderste diameter. Trykket, som pumpemediet udøver i sporet, vil da trykke det elastiske element indefter mod den inderste diameter af sporet. Samtidigt vil trykket, 30 som pumpemediet udøver i sporet, trykke det slidstærke element udefter mod sidevæg- 4 DK 172177 B1 gen. Effektiviteten af tætningen vil da forøges for både det elastiske element og det slidstærke element, når trykket i pumpemediet forøges.Pressure pumping medium directed against the sealing member will be fed into the groove at its outer diameter. The pressure exerted by the pumping medium in the groove will then push the elastic member inward towards the inner diameter of the groove. At the same time, the pressure exerted by the pumping medium in the groove will push the durable element outwards against the sidewall. The effectiveness of the seal will then increase for both the elastic member and the durable member as the pressure in the pumping medium increases.

En alternativ aksial tætning ifølge opfindelsen er særpræget ved, at tætningen er tilveje-5 bragt mellem en første flade og en anden flade, der er beregnet til at foretage en relativ bevægelse, at tætningen mellem fladerne er anbragt i en reces i den første eller den anden flade, at tætningen er dannet af et fleksibelt element, der ligger an mod den første flade, og et stift element, der ligger an mod den anden flade, og at det fleksible element yder en trykkraft mod det stive element.An alternative axial seal according to the invention is characterized in that the seal is provided between a first face and a second face intended to make a relative movement, that the seal between the faces is placed in a recess in the first or the second face. second, that the seal is formed by a flexible member abutting the first face and a rigid member abutting the second face and that the flexible member exerts a compressive force against the rigid member.

1010

Opfindelsen vil herefter blive beskrevet nærmere under henvisning til den medfølgende tegning, hvor fig. 1 er et snit gennem en pumpe med en første udførelsesform for en aksial 15 tætning ifølge opfindelsen, fig. 2 et et snit gennem pumpen illustreret i fig. 1 med afbildning af et indre tandhjul og et ydre tandhjul, der udgør pumpehjul fig. 3 er et snit gennem en del af et pumpekammer og et pumpehjul i en pumpe som illustreret i fig. 1, 20 fig. 4 er et snit gennem en del af et pumpekammer og et pumpehjul i en pumpe som illustreret i fig. 1 og med en anden udførelsesform for en aksial tætning ifølge opfindelsen, fig. 5 er et snit gennem en del af et pumpekammer og et pumpehjul i en pumpe som illustreret i fig. 1 og med en tredje udførelsesform for en aksial 25 tætning ifølge opfindelsen, fig. 6 er et snit gennem en del af et pumpekammer og et pumpehjul i en pumpe som illustreret i fig. 1 og med en fjerde udførelsesform for en aksial tætning ifølge opfindelsen, fig. 7 er et snit gennem første udførelsesformer for en massiv ring og en 30 fleksibel ring i en aksial tætning ifølge opfindelsen, 5 DK 172177 B1 fig. 8 er et snit gennem andre udførelsesformer for en massiv ring og en fleksibel ring i en aksial tætning ifølge opfindelsen, og fig. 9 er et snit gennem tredje udførelsesformer for en massiv ring og en fleksi bel ring i en aksial tætning ifølge opfindelsen.The invention will now be described in more detail with reference to the accompanying drawing, in which fig. 1 is a section through a pump having a first embodiment of an axial seal according to the invention; FIG. 2 is a section through the pump illustrated in FIG. 1 with an internal sprocket and an outer sprocket constituting an impeller; FIG. 3 is a section through a portion of a pump chamber and impeller in a pump as illustrated in FIG. 1, 20 FIG. 4 is a section through a portion of a pump chamber and impeller in a pump as illustrated in FIG. 1 and with another embodiment of an axial seal according to the invention; FIG. 5 is a section through a portion of a pump chamber and impeller in a pump as illustrated in FIG. 1 and with a third embodiment of an axial seal according to the invention, fig. 6 is a section through a portion of a pump chamber and impeller in a pump as illustrated in FIG. 1 and with a fourth embodiment of an axial seal according to the invention; 7 is a section through first embodiments of a solid ring and a flexible ring in an axial seal according to the invention; FIG. 8 is a section through other embodiments of a solid ring and a flexible ring in an axial seal according to the invention; and FIG. 9 is a section through third embodiments of a solid ring and a flexible ring in an axial seal according to the invention.

55

Fig. 1 illustrerer ved et snit en pumpe med en aksial tætning ifølge opfindelsen. Pumpen omfatter et pumpehus 1. En omdrejningsaksel 2 er understøttet i lejer 3,4 og strækker sig ind i pumpehuset 1 gennem en første sidevæg 5. Sidevæggen 5 danner sammen med en anden sidevæg 6 aksial afgrænsning af et pumpekammer 7. Pumpehuset 1 omfatter 10 en kammervæg 8. Kammervæggen 8 danner lejering for et en ydre tandkrans 26, der ligeledes danner afgrænsning af pumpekammeret 7. Et roterende element i form af et indre tandhjul 9 er anbragt i pumpekammeret 7. Det indre tandhjul 9 er monteret på omdrejningsakslen 2 og er beregnet til at blive drevet af omdrejningsakslen 2. Mellem omdrejningsakslen 2 og det indre tandhjul 9 er derfor monteret en feder 10. Pumpen, der er 15 illustreret i figuren, er en gerotorpumpe, som fungerer ved, at et medium pumpes ved succesivt indgreb mellem tænderne på det indre tandhjul 9 henholdsvis den ydre tandkrans 26 (se fig. 2). I det følgende vil det indre tandhjul blive benævnt pumpehjulet.FIG. 1 is a sectional view illustrating a pump with an axial seal according to the invention. The pump comprises a pump housing 1. A rotary shaft 2 is supported in bearings 3,4 and extends into the pump housing 1 through a first side wall 5. The side wall 5 together with a second side wall 6 forms an axial demarcation of a pump chamber 7. The pump housing 1 comprises a chamber wall 8. The chamber wall 8 forms a bearing for an outer tooth ring 26, which also forms the boundary of the pump chamber 7. A rotating element in the form of an internal sprocket 9 is arranged in the pump chamber 7. The internal sprocket 9 is mounted on the shaft 2 and is intended to to be driven by the shaft 2. Between the shaft 2 and the internal sprocket 9 is therefore mounted a spring 10. The pump illustrated in the figure is a gerotor pump which operates by pumping a medium by successively engaging the teeth of the internal sprocket 9 and the outer sprocket 26, respectively (see Fig. 2). In the following, the internal sprocket will be referred to as the impeller.

Den første sidevæg er forsynet med en gennemgangshul 11 for omdrejningsakslen. Den 20 anden sidevæg er forsynet med et indløb 12 til pumpekammeret 7 og et udløb 13 fra pumpekammeret 7 for det medium, der skal pumpes. Et endedæksel 14 ligger an mod en yderside 15 af den anden sidevæg 6 og er forsynet med gevindhuller 16 for tilslutning af slanger eller rør (ikke vist) til at lede mediet til og fra pumpen. Mellem den første sidevæg 5 og kammervæggen 8, mellem kammervæggen 8 og den anden sidevæg 6 og 25 mellem den anden sidevæg 6 og endedækslet 14 er tætningselementer 17 anbragt i spor 18. Mellem omdrejningsakslen 2 og pumpehjulet 9 er anbragt et yderligere tætningselement 27. Tætningselementet 27 er anbragt i et spor 28 i omdrejningsakslen Tætningselementeme 17 og 27 er i den viste pumpe pakningsringe, fortrinsvis O-ringe.The first sidewall is provided with a through-hole 11 for the shaft. The second second side wall is provided with an inlet 12 for the pump chamber 7 and an outlet 13 from the pump chamber 7 for the medium to be pumped. An end cap 14 abuts an outside surface 15 of the second side wall 6 and is provided with threaded holes 16 for connecting hoses or tubes (not shown) to guide the medium to and from the pump. Between the first sidewall 5 and the chamber wall 8, between the chamber wall 8 and the second sidewall 6 and 25 between the second sidewall 6 and the end cover 14, sealing elements 17 are arranged in groove 18. Between the rotary shaft 2 and the impeller 9, a further sealing element 27. The sealing element 27 is arranged. is disposed in a groove 28 in the rotary shaft Sealing elements 17 and 27 are in the pump shown, seal rings, preferably O-rings.

30 Mellem den første sidevæg 5 og pumpehjulet 9 er ligeledes anbragt et tætningselement 19. Tætningselementet 19 udgør den aksiale tætning ifølge opfindelsen. Tætningsele- 6 DK 172177 B1 mentet 19 består i den viste udførelsesform af en massiv ring 20 og en elastisk ring 21. Taetningselementet er anbragt i et spor 22 i pumpehjulet 9. Den elastiske ring 21 er anbragt i en bund 23 (se fig. 3) af sporet 22 og den massive ring 20 er anbragt mellem den elastiske ring 21 og den første sidevæg 5 således, at den massive ring 20 strækker sig 5 udenfor en åbning 24 (se fig. 3) for sporet 22 og ligger an mod den første sidevæg 5. Den massive ring 20 er beregnet til at danne tætning mellem ringen 20 og den første sidevæg 5 og til at optage slidbelastninger ved pumpehjulet 9’s rotation i pumpekammeret 7. Den elastiske ring 21 er beregnet til at danne tætning mellem pumpehjulet 9 og den massive ring 20 og til at etablere en tilstrækkelig anlægskraft for den massive ring 10 20’s anlæg mod den første sidevæg 5.30 Between the first side wall 5 and the impeller 9 there is also arranged a sealing element 19. The sealing element 19 constitutes the axial seal according to the invention. The sealing element 19 in the illustrated embodiment consists of a solid ring 20 and an elastic ring 21. The sealing element is arranged in a groove 22 in the impeller 9. The elastic ring 21 is arranged in a bottom 23 (see Fig. 3 ) of the groove 22 and the solid ring 20 are disposed between the elastic ring 21 and the first sidewall 5 such that the solid ring 20 extends 5 outside an opening 24 (see Fig. 3) of the groove 22 and abuts the first sidewall 5. The solid ring 20 is intended to form a seal between the ring 20 and the first sidewall 5 and to accommodate wear loads during the rotation of the impeller 9 in the pump chamber 7. The elastic ring 21 is intended to form a seal between the impeller 9 and the solid ring 20 and to establish a sufficient abutment force for the abutment of the massive ring 10 20 against the first sidewall 5.

Den massive ring 20 er fortrinsvis fremstillet af et materiale, der indeholder kul, kulfibre eller grafit eller som alternativt er belagt med eller fremstillet af teflon® eller PEEK for at minimere friktion mellem ringen 20 og den første sidevæg 5. Den elastiske ring 21 er 15 fortrinsvis fremstillet af gummi.The solid ring 20 is preferably made of a material containing coal, carbon fiber or graphite or alternatively coated with or made of teflon® or PEEK to minimize friction between the ring 20 and the first sidewall 5. The elastic ring 21 is 15 preferably made of rubber.

Fig. 2 illustrerer et snit gennem gerotorpumpen i fig. 1. Snittet er rettet vinkelret i forhold til snittet i fig. 1 og forløber gennem pumpekammeret 7. Figuren illustrerer omdrejningsakslen 2, det indre pumpehjul 9, den ydre tandkrans 26 og pumpekammeret 7 20 mellem det indre pumpehjul 9 og den ydre tandkrans 26.Kammervæggen 8 og den anden sideplade 6, indløbet 12 og udløbet 13 samt sporet 22 er ligeledes illustreret.FIG. 2 illustrates a section through the gerotor pump of FIG. 1. The incision is directed perpendicular to the incision of FIG. 1 and extends through the pump chamber 7. The figure illustrates the shaft 2, the inner impeller 9, the outer tooth ring 26 and the pump chamber 7 20 between the inner impeller 9 and the outer tooth ring 26. The chamber wall 8 and the second side plate 6, the inlet 12 and the outlet 13 and the groove 22 is also illustrated.

Fig. 3 illustrerer ved et snit et forstørret udsnit af pumpen illustreret i fig. 1. Fig. 3 illustrerer omdrejningsakslen 2, den første sidevæg 5, den anden sidevæg 6 med indløb 12, 25 kammervæggen 8, pumpekammeret 7, pumpehjulet 9, tætningselementer 17 mellem kammervæggen 8 og den første sidevæg 5 henholdsvis den anden sidevæg 6 samt tætningselement 27 mellem omdrejningsakslen og pumpehjulet 9. Den aksiale tætning 19 ifølge opfindelsen er ligeledes illustreret. Pumpehjulet 9 har en første sideflade 9’, der er modsatstående den første sidevæg 5, og en anden sideflade 9”, der er modsatstående 30 den anden sidevæg 6.FIG. 3 is a sectional view showing an enlarged section of the pump illustrated in FIG. 1. FIG. 3 illustrates the shaft 2, the first sidewall 5, the second sidewall 6 with inlet 12, the chamber wall 8, the pump chamber 7, the impeller 9, the sealing elements 17 between the chamber wall 8 and the first sidewall 5, respectively, the second sidewall 6, and the sealing element 27 between the pivot shaft and the impeller. 9. The axial seal 19 of the invention is also illustrated. The impeller 9 has a first side surface 9 'opposite the first side wall 5 and a second side surface 9' opposite the second side wall 6.

7 DK 172177 B17 DK 172177 B1

Den aksiale tætning består som nævnt af en massiv ring 20 og en elastisk ring 21. Den elastiske ring 21 er anbragt i bunden 23 af sporet 22 og har en mindste diameter 421, der er stort set lig en mindste diameter d22 af sporet 22, og en største diameter D2i, der er mindre end en største diameter D22 af sporet 22. Den massive ring 20 er anbragt ved 5 åbningen 24 af sporet 22 og har en mindste diameter d20 henholdsvis en største diameter D20, der befinder sig mellem den mindste diameter d22 henholdsvis den største diameter D22 af sporet 22.As mentioned, the axial seal consists of a solid ring 20 and an elastic ring 21. The elastic ring 21 is disposed at the bottom 23 of the groove 22 and has a minimum diameter 421 which is substantially equal to a minimum diameter d22 of the groove 22, and a larger diameter D2i smaller than a largest diameter D22 of the groove 22. The solid ring 20 is arranged at the opening 24 of the groove 22 and has a minimum diameter d20 and a largest diameter D20, respectively, between the smallest diameter d22 respectively the largest diameter D22 of the groove 22.

Fig. 4 illustrerer en anden udførelsesform for en aksial tætning ifølge opfindelsen. Den 10 aksiale tætning består i denne udførelsesform af et første tætningselement 19’ mellem pumpehjulet 9 og den første sidevæg 5 og et andet tætningselement 19” mellem pumpehjulet 9 og den anden sidevæg 6. Tætningselementeme 19’ og 19” er de samme som tætningselementet 19 beskrevet i fig. 3. Der henvises således til fig. 3 for beskrivelse af tætningselementeme i fig. 4.FIG. 4 illustrates another embodiment of an axial seal according to the invention. The 10 axial seal in this embodiment consists of a first sealing element 19 'between the impeller 9 and the first side wall 5 and a second sealing element 19 "between the impeller 9 and the second side wall 6. The sealing elements 19' and 19" are the same as the sealing element 19 described. in FIG. 3. Referring now to FIG. 3 for describing the sealing elements of FIG. 4th

1515

Fig. 5 illustrerer en tredje udførelsesform for en aksial tætning ifølge opfindelsen. I den viste udførelsesform er tætningen mellem den første sidevæg 5 og pumpehjulet 9 tilvejebragt ved det første tætningselement 19’ som illustreret i fig. 4, men hvor sporet 22 er tilvejebragt i den første sidevæg 5 frem for i pumpehjulet 9. Notgangen 22 for det andet 20 tætningselement 19” mellem pumpehjulet 9 og den anden sidevæg 6 er stadig tilvejebragt i pumpehjulet 9, men kunne i en alternativ udførelsesform være tilvejebragt i den anden sidevæg 6. Tætningselementeme 19’ og 19” er de samme som tætningselementet 19 beskrevet i fig. 3. Der henvises således til fig. 3 for beskrivelse af tætningselementeme i fig. 5.FIG. 5 illustrates a third embodiment of an axial seal according to the invention. In the illustrated embodiment, the seal between the first side wall 5 and the impeller 9 is provided by the first seal element 19 'as illustrated in FIG. 4, but where the groove 22 is provided in the first side wall 5 rather than in the impeller 9. The groove 22 for the second 20 sealing element 19 "between the impeller 9 and the second side wall 6 is still provided in the impeller 9, but in an alternative embodiment could be provided in the second sidewall 6. The sealing members 19 'and 19 "are the same as the sealing member 19 described in FIG. 3. Referring now to FIG. 3 for describing the sealing elements of FIG. 5th

2525

Fig. 6 illustrerer en fjerde udførelsesform for en aksial tætning ifølge opfindelsen. Den aksiale tætning er i denne udførelsesform tilvejebragt dels mellem pumpehjulet 9 og den første sidevæg 5 henholdsvis den anden sidevæg 6, og dels mellem den ydre tandkrans 26 og den første sidevæg 5 henholdsvis den anden sidevæg 6. Tætningselementeme er 30 de samme som tætningselementet beskrevet i fig. 3. Der henvises således til fig. 3 for beskrivelse af tætningselementeme i fig. 6.FIG. 6 illustrates a fourth embodiment of an axial seal according to the invention. In this embodiment, the axial seal is provided partly between the impeller 9 and the first sidewall 5 and the second sidewall 6, respectively, and partly between the outer tooth rim 26 and the first sidewall 5 and the second sidewall 6. The sealing elements 30 are the same as the sealing element described in FIG. FIG. 3. Referring now to FIG. 3 for describing the sealing elements of FIG. 6th

DK 172177 Bl gDK 172177 Bl g

Fig. 7 illustrerer i snit de tætningselementer, der er illustreret i fig. 3-6. Tætningselementet 19 består således af en massiv ring 20 og en elastiske ring 21. Den elastiske ring 21 har en mindste diameter d2i der lig med, alternativt mindre end, den mindste diameter d22 af sporet 22, og en største diameter D21, der er mindre end den største diameter 5 D22 af sporet 22. Den massive ring 20 har en mindste diameter d20 henholdsvis en største diameter D20, der befinder sig mellem den mindste diameter d22 henholdsvis den største diameter D22 af sporet 22.FIG. 7 illustrates in section the sealing elements illustrated in FIG. 3-6. Thus, the sealing member 19 consists of a solid ring 20 and an elastic ring 21. The elastic ring 21 has a minimum diameter d2i equal to, alternatively smaller than, the smallest diameter d22 of the groove 22, and a largest diameter D21 less than the largest diameter 5 D22 of the groove 22. The solid ring 20 has a minimum diameter d20 and a largest diameter D20, respectively, located between the smallest diameter d22 and the largest diameter D22 of the groove 22, respectively.

Ved at den elastiske ring 21 har en mindste diameter d2„ der er stort set lig en mindste 10 diameter d22 for sporet 22, og en største diameter D21, der er mindre end en største diameter D22 for sporet 22, forbedres de tætnede egenskaber af den elastiske ring 21. Såfremt medium, der pumpes, ledes fra pumpekammeret 7 forbi pumpehjulets anlæg 25 med den første sidevæg 5 og ind i sporet 22, vil dette medium, der er under tryk, udøve et tryk på den elastiske ring 21 indefter mod den mindste diameter d22 af sporet 22. Ef-15 tersom den mindste diameter d21 af den elastiske ring 21 er lig den mindste diameter d22 af sporet 22, vil den elastiske ring 21 på grund af det tryk, som mediet under tryk påvirker ringen 21 med, deformeres således, at ringen 21 presses indefter mod bunden 23 af sporet 22 og udefter mod den massive ring 20. Dette pres mod bunden 23 af sporet 22 henholdsvis den massive ring 20 forøger den tætnende effekt af den elastiske ring 21 og 20 ydermere den tætnende effekt af den massive ring 20’s anlæg mod den første sidevæg 5.By having the elastic ring 21 having a minimum diameter d2, which is substantially equal to a minimum diameter d22 for the groove 22, and a larger diameter D21 smaller than a larger diameter D22 for the groove 22, the sealed properties of the elastic ring 21. If medium being pumped is passed from the pump chamber 7 past the impeller system 25 with the first side wall 5 and into the groove 22, this pressurized medium will exert pressure on the elastic ring 21 inwardly toward the smallest diameter d22 of the groove 22. If the smallest diameter d21 of the elastic ring 21 is equal to the smallest diameter d22 of the groove 22, the elastic ring 21 due to the pressure with which the medium under pressure affects the ring 21 will deform so that the ring 21 is pressed inwardly towards the bottom 23 of the groove 22 and outwardly against the solid ring 20. This pressure against the bottom 23 of the groove 22 and the solid ring 20, respectively, further increases the sealing effect of the elastic ring 21 and 20 further to the sealing end. e effect of the massive ring 20's abutment against the first sidewall 5.

Desuden vil det tryk, som mediet udøver i sporet 22, også presse den massive ring 20 yderligere ud mod den første sidevæg 5. Den elastiske ring 21 sikrer tilstrækkelig tætning ved stilstand af pumpen, mens trykket af mediet sikrer forøget tæning under drift.In addition, the pressure exerted by the medium in the groove 22 will also further exert the massive ring 20 toward the first sidewall 5. The elastic ring 21 ensures adequate sealing at the pump stop while the pressure of the medium ensures increased sealing during operation.

25 Fig. 8 illustrerer en anden udførelsesform for den massive ring 20, der udgør en del af den aksiale tætning ifølge opfindelsen. Den massive ring 20 har i denne udførelsesform form som et L. Herved opnås lettere montage af den elastiske ring 21, idet den elastiske ring 21 sikres korrekt placering i forhold til den massive ring 20.FIG. 8 illustrates another embodiment of the solid ring 20 which forms part of the axial seal of the invention. In this embodiment, the solid ring 20 is shaped like an L. This facilitates easier mounting of the elastic ring 21, ensuring that the elastic ring 21 is positioned correctly relative to the solid ring 20.

30 Fig. 9 illustrerer en anden udførelsesform for den massive ring 20, der udgør en del af den aksiale tætning ifølge opfindelsen. Den massive ring 20 har i denne udførelsesform 9 DK 172177 B1 form som et U. Ligeledes her opnås lettere montage af den elastiske ring 21, og ydermere er det muligt at formontere den elastiske ring 21 og den massive ring 20 således, at disse danner ét og samme element.FIG. 9 illustrates another embodiment of the solid ring 20 which forms part of the axial seal of the invention. In this embodiment, the solid ring 20 is in the form of a U. In this case, easier assembly of the elastic ring 21 is also achieved, and furthermore it is possible to pre-assemble the elastic ring 21 and the massive ring 20 to form one. and the same element.

5 Den aksiale tætning ifølge opfindelsen er i det ovenstående beskrevet under henvisning til en specifik udførelsesform for en pumpe og under henvisning til en specifik udførelsesform for et tætningselement bestående af en massiv ring og en elastisk ring. Det vil imidlertid være muligt at anvende den aksiale tætning i andre typer pumper end den illustrerede. Således vil det være muligt at tilvejebringe indløb i den anden sidevæg og 10 udløb i den første sidevæg, indløb i den første sidevæg og udløbe i den anden sidevæg eller både indløb og udløb i den første sidevæg. Andre udførelsesformer for den aksiale tætning vil ligeledes kunne tilvejebringes.The axial seal according to the invention is described above with reference to a specific embodiment of a pump and with reference to a specific embodiment of a sealing element consisting of a solid ring and an elastic ring. However, it will be possible to use the axial seal in other types of pumps than the one illustrated. Thus, it will be possible to provide inlet in the second sidewall and outlet in the first sidewall, inlet in the first sidewall and outlet in the second sidewall or both inlet and outlet in the first sidewall. Other embodiments of the axial seal may also be provided.

Claims

An axial seal in a pump or motor comprising a housing (1) with side walls (5,6) defining an axial extension for a chamber (7) and of which side walls (5,6) at least 5 one has an inlet (12) and optionally an outlet (13), the pump or motor also comprising a shaft (2) extending through at least one shaft hole (11) in one side wall (5), a rotating element (9) located between the sidewalls (5,6) and having a first sidewall (9 ') opposed to one sidewall (5) and a second sidewall (9 ") opposed to the other side wall (6), which rotating element (9) is intended to be rotated by the shaft (2), and at least one sealing element (19) located between and abutting an inside of a side wall (5, 6) and a side face of the rotating element, characterized in that the sealing element (19) extends around the rotary shaft (2) and that the sealing element (19) in radial direction g is disposed between the shaft (2) and the inlet (12), the optional outlet (13).

Axial seal according to claim 1, characterized in that the second side wall (6) is provided with an inlet (12), the second side wall (6) is also provided with an outlet (13), that a first sealing element (19) ) is disposed between the first side face (9 ') of the rotating member (9) and the first side wall (5) and the sealing member (19) extends radially between the shaft (2) and the inlet (12). .

Axial seal according to claim 1, characterized in that the second side wall (6) is provided with an inlet (12), the first side wall (5) is provided with an outlet (13), at least one first sealing element ( 19) is disposed between the first side surface (9 ') of the rotating element (9) and the first side wall (5), and at least one second sealing element (19) is disposed between the second side surface (9 ") of the rotating element (9). 9) and the second side wall (6) and that the sealing elements (19) extend radially between the shaft (2) and the inlet (12) and the outlet (13), respectively. 30 11 DK 172177 B1

Axial seal according to any of the preceding claims, characterized in that the seal comprises a first circular seal element (19 ') and a second circular seal element (19'), the first seal element (19 ') being disposed between the first side wall (5) and first side surface (9 ') of the rotating element (9), and the second sealing element (19 ") is arranged between the second side wall (6) and the second side surface (9") thereof. rotating member (9) and at least the first sealing member (19 ') extending around the shaft.

Axial seal according to claim 3, characterized in that the second sidewall (6) is provided with an inlet (12), that the first sidewall (5) is provided with an outlet (13), that the second sidewall (6) is also provided with a shaft hole, that the shaft (2) extends through the shaft hole (11) in the first sidewall (5), through the rotating element (9) and through the shaft hole in the second sidewall (6), and the first sealing member (19 ') extends around the shaft (2) and in a radial direction between the shaft (2) and the outlet (13), and the second sealing member (19 ") extends around the shaft (2) and in a radial direction between the shaft (2) and the inlet (12).

Axial seal according to any one of the preceding claims, characterized in that the sealing element consists of a ring (20) made of a carbonaceous material, alternatively made of preferably polytetrafluoroethene, alternatively of PEEK, and an adjacent elastic. ring (21) made of a different material, preferably rubber, and the solid ring (20) and elastic ring (21) having a substantially common circumference. 25

Axial seal according to any one of the preceding claims, characterized in that at least one of the first and the other respectively of the side surfaces (9 ', 9') of the rotating element (9) is provided with a groove ( 22) extending about the shaft (2), and a sealing element (19) disposed in the groove and extending outside an opening (24) in the groove (22) and abutting the opposite side wall (5). , 6). 12 DK 172177 B1

Axial seal according to any one of the preceding claims, characterized in that the rotating element (9) is provided with a first groove (22) extending on the first side surface (9 ') of the rotating element (9). 9), and a second groove (22) extending on the second side surface (9 ") of the rotating element (9), a first sealing ring 5 (19 ') is provided in the first groove (22) and a a second sealing ring (19 ”) in the second groove (22), and that the first sealing ring is in contact with the first side wall of the housing and the second sealing ring is in contact with the second side wall of the housing.

Axial seal according to any one of claims 6 to 8, characterized in that the elastic ring (21) has a minimum diameter (d2i) less than or equal to a minimum diameter (d22) of the groove ( 22) that the elastic ring (21) has a largest diameter (D2i) smaller than a larger diameter (D22) of the groove (22), that the elastic ring (21) is arranged in a bottom (23) of the groove (22) and that the solid ring (20) is disposed between the elastic ring (21) and an opposite side wall (5,6) and extends outside an opening (24) for the groove (22).

An axial seal in a pump or motor, characterized in that the seal is provided between a first face and a second face intended to make a relative movement, that the seal between the faces is placed in a recess in the first or second face. 20, that the seal is formed by a flexible member abutting the first face and a rigid member abutting the second face and that the flexible member exerts a compressive force against the rigid member.